WO2021032708A1 - Machine électrique pour un véhicule à moteur - Google Patents

Machine électrique pour un véhicule à moteur Download PDF

Info

Publication number
WO2021032708A1
WO2021032708A1 PCT/EP2020/073052 EP2020073052W WO2021032708A1 WO 2021032708 A1 WO2021032708 A1 WO 2021032708A1 EP 2020073052 W EP2020073052 W EP 2020073052W WO 2021032708 A1 WO2021032708 A1 WO 2021032708A1
Authority
WO
WIPO (PCT)
Prior art keywords
rotor
bearing
electrical machine
receiving
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2020/073052
Other languages
German (de)
English (en)
Inventor
Isao Fukumoto
Matti RADWAINSKI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Vitesco Technologies Germany GmbH
Original Assignee
Vitesco Technologies Germany GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Vitesco Technologies Germany GmbH filed Critical Vitesco Technologies Germany GmbH
Publication of WO2021032708A1 publication Critical patent/WO2021032708A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/086—Structural association with bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
    • H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
    • H02K5/1737—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans
    • H02K7/16—Structural association with mechanical loads, e.g. with hand-held machine tools or fans for operation above the critical speed of vibration of the rotating parts

Definitions

  • Electric machines for at least partially electrically driven motor vehicles are known in principle. Such electrical machines are subject to high loads due to the high speeds of more than 12,000 rpm. In addition, such electrical machines should be quiet so that third parties or the driver are not unnecessarily annoyed by the noises of the electric motor. Furthermore, there is an endeavor to build the electrical machine as light as possible so that the overall performance of the motor vehicle can be increased. The endeavor to save weight on the electrical machine can lead to components of the electrical machine, in particular the rotor shaft, being of more filigree design and thus being able to have increased elasticity. Coupled with a high speed level of the electrical machines and the presence of residual imbalances, the rotor shaft can be made to vibrate, which causes or can cause undesired noises.
  • an electrical machine for an at least partially electrically driven motor vehicle with a stator housing having a receiving opening, a hollow-cylindrical stator connected in a rotationally fixed manner in the stator housing, and one inside the stator via an air gap to an inner lateral surface of the stator spaced-apart rotor which has a rotor hollow shaft, a gear housing with a gear input shaft mounted in the gear housing, the rotor hollow shaft and the gear input shaft being rotatably connected to one another, and a bearing plate having a bearing mandrel, the bearing mandrel engaging in a hollow shaft opening of the rotor hollow shaft that engages on a the side of the rotor facing away from the transmission input shaft is formed, and the end shield closes the receiving opening of the stator housing, the rotor being rotatably mounted on the bearing mandrel via a pivoted bearing device.
  • an electrical machine for an at least partially electrically driven motor vehicle.
  • the electrical machine has a stator housing.
  • the stator housing comprises a cylindrical inner jacket surface.
  • the stator housing has a receiving opening which is formed in the axial direction starting from a longitudinal axis of the stator housing.
  • a hollow-cylindrical stator is arranged in a rotationally fixed manner in the stator housing.
  • Non-rotatably means that the stator arranged in the stator housing does not experience any rotation in the circumferential direction relative to the stator housing during operation of the electrical machine.
  • a rotor is arranged inside the stator, which is arranged at a distance from the inner circumferential surface of the stator via an air gap and has a hollow rotor shaft.
  • the electric machine also includes a transmission housing with a transmission input shaft mounted in the transmission housing, the rotor hollow shaft and the transmission input shaft being connected to one another in a rotationally fixed manner.
  • a bearing plate which has a bearing pin, closes the receiving opening of the stator housing.
  • the bearing mandrel engages in a hollow shaft opening of the rotor hollow shaft, the hollow shaft opening being formed on a side of the rotor facing away from the transmission input shaft.
  • the rotor is rotatably mounted on the bearing mandrel via a pivoted bearing device.
  • a longitudinal direction of the bearing mandrel runs coaxially to the longitudinal direction of the transmission input shaft. Manufacturing-related tolerances or slight deviations from the longitudinal direction between the bearing mandrel and the transmission input shaft can be compensated for via the pivoted bearing device.
  • the swivel joint design of the bearing device provides, on the one hand, a bearing for rotating the rotor about its longitudinal axis.
  • tolerance compensation in the longitudinal direction of the rotor can, for example, be provided by the pivot joint mounting, since, for example, an inner bearing ring can be pivoted relative to an outer bearing ring of the bearing device perpendicular to the longitudinal direction of the bearing device.
  • the swivel bearing device has a spherical bearing. This compensation can increase undesired noises during operation of the electrical machine and the longevity of the electrical machine.
  • the air gap can be reduced due to the pivoting joint design between the rotor and stator, since manufacturing-related tolerances can be compensated. The power density of the electrical machine can thus be increased.
  • the pivotably connected bearing device has a receiving ring for arrangement in the rotor hollow shaft and for receiving a bearing, the receiving ring having an inner surface on a side facing the bearing, which is concave in the axial direction of the receiving ring comprises, and the bearing on a side facing the inner circumferential surface of the receiving ring comprises an outer circumferential surface which has a convex configuration in the axial direction of the bearing.
  • the circumferential surface of the receiving ring directed inward in the radial direction has a concave geometry in a longitudinal section
  • the bearing has a convex shape on its circumferential surface directed outward in the radial direction, so that the bearing is arranged spherically in the receiving ring and / or is stored.
  • the receiving ring is designed in such a way that the bearing can be arranged and / or positioned in the receiving ring via a translational movement and via a pivoting movement.
  • the bearing is arranged such that the longitudinal direction of the bearing is arranged at an angle of 90 ° to the longitudinal direction of the receiving ring.
  • the bearing is inserted into the receiving ring by a translatory movement.
  • the receiving ring has two spaced apart receiving grooves for receiving the bearing on an end face aligned in the axial direction of the receiving ring, so that the bearing can be arranged in the receiving ring and subsequently pivoted preferably via a translational movement.
  • the bearing device is mounted and / or designed to be damping.
  • the receiving ring preferably has an inner first ring and an outer second ring, the first ring having a reduced diameter compared to the second ring, and the first ring being connected to the second ring via at least one strut.
  • the first ring and the second ring are preferably in one plane.
  • the at least one strut is advantageously aligned in the radial direction of the first ring and / or second ring. Is particularly advantageous it is provided that the first ring is connected to the second ring via a plurality of struts which are arranged at a distance from one another in the circumferential direction.
  • the damping of the bearing device can be adjusted via the cross section, the number and the length of the struts between the first and the second ring. It is also conceivable that damping can be achieved via the material of the receiving ring. If the bearing device is arranged as a fixed bearing in the bearing seat of the hollow rotor shaft, axial vibrations of the hollow rotor shaft can be damped via the receiving ring, in particular via the struts between the first ring and the second ring. In this way, tolerance-related vibrations of the rotor can consequently be dampened and / or absorbed via the bearing device during operation. In addition, noise from the rotor can be counteracted.
  • the bearing can be designed in such a way that it enables the rotor to be mounted on the bearing mandrel so that it can be rotated about its longitudinal axis.
  • An advantageous further development of the invention is that the bearing is designed as a roller bearing, roller bearing and / or needle bearing. Such bearings can be produced inexpensively and are more robust. In this way, inexpensive and long-lasting storage of the rotor can be provided.
  • the bearing device is arranged in the longitudinal direction of the rotor in the area of the rotor's center of gravity.
  • the loads of the rotor can be optimally transferred to the bearing mandrel and introduced into it.
  • an advantageous development of the invention provides that the hollow rotor shaft is cast onto an inner jacket surface of an annular laminated core, or the hollow rotor shaft is pressed and / or molded into the annular laminated core.
  • two possibilities are provided for how the hollow rotor shaft can be connected to the laminated core of the rotor in a simple manner in a rotationally fixed manner. Due to the fact that the rotor has a hollow rotor shaft, the rotor in the region of the laminated core arranged on the hollow rotor shaft contains only as much iron as is necessary for magnetic reasons. This results in a rotor with an optimized mass inertia based on the gravimetric and rotational properties.
  • the hollow rotor shaft is formed from an aluminum alloy and / or comprises aluminum.
  • forged hollow rotor shafts which are pressed into and / or molded onto the ring-shaped laminated core of the rotor, preferably have an aluminum alloy.
  • a hollow rotor shaft made of an aluminum alloy can have increased strength and thermal conductivity compared to cast hollow rotor shafts, which are preferably formed from an aluminum casting, so that the rotor stiffness can be increased, whereby noise can be reduced during operation.
  • there is no phase change heat in forged hollow rotor shafts that are formed onto the laminated core so that the thermal load on the rotor is reduced. This means that premagnetized magnets can also be arranged in the rotor, so that the manufacturing process can be accelerated.
  • the rotor is preloaded in the axial direction.
  • the preload can increase the stiffness of the rotor, so that vibrations of the rotor caused by elasticity can be reduced.
  • the pretensioning of the rotor or the laminated core can preferably take place via tie rods which are guided through the laminated core and pretension it in the axial direction of the rotor.
  • the laminated core is pretensioned before the hollow rotor shaft is cast on and the pretensioning is held by the hollow rotor shaft cast on.
  • the laminated core is pretensioned before the forged hollow rotor shaft is formed onto the laminated core, and the pretensioning is maintained by the shape of the hollow rotor shaft formed onto the laminated core.
  • the invention also relates to the use of the electrical machine according to the invention in an at least partially electrically driven vehicle.
  • the invention also relates to a vehicle with the electrical machine according to the invention.
  • FIG. 1 shows a longitudinal section through an electrical machine according to a preferred exemplary embodiment of the invention
  • FIG. 2 shows a three-dimensional representation of a laminated core of a rotor of the electrical machine
  • FIG. 3 shows a section through the rotor of the electrical machine with a cast-on hollow rotor shaft
  • FIG. 4 shows a view of the laminated core with a forged hollow rotor shaft
  • FIG. 5 shows a three-dimensional view of the rotor with a forging die for forming the hollow rotor shaft onto the laminated core
  • 6 shows a three-dimensional view of a pivot-connected bearing device in the rotor hollow shaft; 7 to 9 each show a view of the arrangement of a bearing in a receiving ring of the bearing device;
  • the electrical machine 10 for an at least partially electrically driven motor vehicle.
  • the electrical machine 10 has a stator housing 12.
  • the stator housing 12 comprises a cylindrical inner jacket surface 14, which is directed inward in the radial direction.
  • the stator housing 12 also has a receiving opening 16, which is formed in the axial direction starting from a longitudinal axis 18 of the stator housing 12.
  • a hollow cylindrical stator 20 is arranged in a rotationally fixed manner.
  • Non-rotatably means that the stator 20 arranged in the stator housing 12 does not experience any rotation in the circumferential direction relative to the stator housing 12 during operation of the electrical machine 10.
  • a rotor 22 is arranged inside the hollow-cylindrical stator 20, which is arranged at a distance from the inner jacket surface 14 of the stator 20 via an air gap.
  • the rotor 22 comprises a hollow rotor shaft 24 and a laminated core 26 which is arranged on the hollow rotor shaft 24 and has a plurality of magnets, which are preferably designed as permanent magnets or permanent magnets.
  • the electric machine 10 also includes a gear housing 28 with a gear input shaft 30 mounted in the gear housing 28.
  • the gear input shaft 30 is rotatably mounted about its longitudinal axis 34 via two bearings 32 arranged at a distance from one another.
  • a bearing plate 36 which has a bearing mandrel 38, closes the receiving opening 16 of the stator housing 12.
  • the bearing mandrel 38 engages in a hollow shaft opening 40 of the rotor hollow shafts 24, the hollow shaft opening 40 is formed on a side of the rotor 22 facing away from the transmission input shaft 30.
  • the rotor 22 is rotatably mounted on the bearing mandrel 38 of the end shield 36 via a pivoted bearing device 42.
  • the longitudinal direction of the bearing mandrel runs coaxially to the longitudinal axis 34 of the transmission input shaft. Manufacturing-related tolerances or slight deviations from the longitudinal direction between the bearing mandrel 38 and the transmission input shaft 30 can be compensated for via the pivotably connected bearing device 42. This compensation can increase undesired noises during operation of the electrical machine 10 and the longevity of the machine 10.
  • FIG. 2 shows a three-dimensional view of the laminated core 26.
  • the laminated core 26 has a plurality of ring-shaped laminated core segments 44 arranged one behind the other in the axial direction.
  • the laminated core segments 44 include pockets 46 distributed in the circumferential direction for receiving magnets.
  • Cover disks 48 are or are arranged on the end of the laminated core 26.
  • FIG. 3 shows a longitudinal section through the rotor 22 in a first embodiment.
  • the rotor 22 comprises the laminated core 26, which has a plurality of laminated core segments 44 arranged next to one another in the axial direction, the cover disks 48 being arranged on the laminated core 26 at the end.
  • the rotor hollow shaft 24 is cast onto the laminated core 26 and the cover disks 48.
  • the rotor hollow shaft 24 consists of an aluminum casting.
  • the hollow rotor shaft 24 has a projection 50 which is set up and designed to engage in the transmission input shaft 30.
  • the rotor hollow shaft 24 On an end side of the rotor 22 facing away from the projection 50, the rotor hollow shaft 24 has the hollow shaft opening 40.
  • a bearing seat 52 for receiving the bearing device 42 is formed within the rotor hollow shaft 24.
  • the bearing seat 52 is formed in the rotor's center of gravity in relation to the longitudinal direction of the rotor 22.
  • the loads of the rotor 22 can thus be optimally transmitted via the bearing device 42 into the bearing mandrel 38 and introduced into it.
  • the rotor 22 can be balanced by removing material from the cover disks 48. This type of balancing is also known as negative balancing, because for balancing, material is not added, as is usual, but removed.
  • FIG. 4 shows a three-dimensional view of the rotor 22 in a second embodiment.
  • a forged hollow rotor shaft 24 made of an aluminum alloy is inserted onto the laminated core 26, which has a plurality of laminated core segments 44 arranged one behind the other in the axial direction and includes cover disks 48 at the ends.
  • FIG. 5 shows a three-dimensional view of the rotor 22 shown in FIG. 4, the hollow rotor shaft 24 being inserted into the laminated core 26, and a forging tool 54 now being introduced into the hollow rotor shaft 24 in order to form it onto the laminated core 26 and the cover disks 48 in this way, that the rotor hollow shaft 24 is connected to the laminated core 26 and the cover plates 48 in a rotationally fixed manner.
  • a forged rotor hollow shaft 24 made of an aluminum alloy has the advantage that it can have increased strength and thermal conductivity, so that the rotor stiffness can be increased, as a result of which noise during operation of the electrical machine can be reduced.
  • premagnetized magnets can also be arranged in the rotor 22 in this way, so that the setting process can be accelerated.
  • FIG. 6 shows a three-dimensional view of the hollow rotor shaft 24 in the area of the bearing seat 52 with the bearing device 42 arranged in the bearing seat 52, the bearing pin 38 engaging in the bearing device 42 at least in sections.
  • the pivotably connected bearing device 42 has a receiving ring 56 for arrangement in the rotor hollow shaft 24 and for receiving a bearing 58.
  • the receiving ring 56 has an inner side on a side facing the bearing 58 Jacket surface 60, which has a concave configuration in the axial direction of the receiving ring 56.
  • the bearing 58 comprises an outer jacket surface 62 which has a convex configuration in the axial direction of the bearing 58.
  • the circumferential surface 60 of the receiving ring 56 directed inward in the radial direction has a concave geometry in a longitudinal section
  • the bearing has a convex shape on its circumferential surface 62 directed outward in the radial direction.
  • FIGS. 7 to 9 each show three-dimensional views of the bearing device 42 and illustrate how the bearing 58 is arranged in the receiving ring 56 so that it is pivotably mounted.
  • the receiving ring 56 has two receiving grooves 66 arranged at a distance from one another for receiving the bearing 58 on an end face 64 aligned in the axial direction of the receiving ring 56.
  • the bearing 58 is introduced into the receiving ring 56 via a translational movement.
  • a longitudinal axis 68 of the bearing 58 is arranged perpendicular to the longitudinal axis 70 of the receiving ring 56.
  • FIG. 8 shows that the bearing 58 was introduced into the receiving ring 56 via the receiving grooves 66 via the translational movement.
  • the bearing 58 is now pivoted by means of a pivoting movement in such a way that the longitudinal axis 68 of the bearing 58 corresponds to the longitudinal axis 70 of the receiving ring 56. This is usually achieved in that the bearing 58 is pivoted through 90 °.
  • FIG. 9 the bearing device 42 is shown after the bearing 58 inserted into the receiving ring 56 has been pivoted and the longitudinal axis 68 of the bearing 58 corresponds to the longitudinal axis 70 of the receiving ring 56.
  • FIG. 9 also shows that the receiving ring 56 of the bearing device 42 has an inner first ring 74 and an outer second ring 76, the first ring 74 having a reduced diameter compared to the second ring 76.
  • the first ring 74 and the second ring 76 lie in one plane.
  • the first ring 74 and the second ring 76 are connected to one another via a plurality of struts 78.
  • the struts 78 are arranged in the radial direction of the first ring 74 and / or second ring 76 and are formed at a distance from one another in the circumferential direction.
  • a damping effect of the bearing device 42 can be achieved via the cross section, the number and the length of the struts 78 between the first ring 74 and the second ring 76. It is also conceivable that damping of the bearing device 42 can be achieved via the material of the receiving ring 42.
  • the bearing device 42 is arranged as a fixed bearing in the bearing seat 52 of the rotor hollow shaft 24, axial vibrations of the rotor hollow shaft 24 can be damped via the receiving ring 56, in particular via the struts 78 between the first ring 74 and the second ring 76. In this way, tolerance-related vibrations of the rotor 22 can consequently be damped and / or absorbed via the bearing device 42 during operation. In addition, the development of noise by the rotor 22 can be counteracted.
  • receiving grooves 66 for receiving the bearing 58 are formed in the first ring 74.
  • FIG. 10 shows how the bearing device 42 is inserted into the rotor hollow shaft 24 via the hollow shaft opening 40.
  • a securing ring 72 is provided which fixes the bearing device 42 in the axial direction of the hollow rotor shaft 24.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Motor Or Generator Frames (AREA)

Abstract

L'invention concerne une machine électrique (10) avec un carter de stator (12) qui présente une ouverture de réception (16) ; un stator (20) qui est fixé en rotation dans le carter de stator (12) et conçu pour être un cylindre creux ; un rotor (22) qui est disposé à l'intérieur du stator (20) à une certaine distance de la surface latérale intérieure (14) du stator (20) de l'autre côté d'un entrefer et comporte un arbre creux de rotor (24) ; un boîtier de transmission (28) avec un arbre d'entrée de transmission (30) qui est monté dans le boîtier de transmission (28), ledit arbre creux de rotor (24) et l'arbre d'entrée de transmission (30) étant reliés l'un à l'autre de manière fixe en rotation ; et un flasque de palier (36) qui comporte une broche de palier (38). La broche de palier (38) se loge dans une ouverture d'arbre creux (40) de l'arbre creux de rotor (24), ladite ouverture d'arbre creux étant formée sur le côté de rotor (22) opposé à l'arbre d'entrée de transmission (30), et le flasque de palier (36) ferme l'ouverture de réception (16) du boîtier de stator (12), le rotor (22) étant monté rotatif sur la broche de palier (38) par l'intermédiaire d'un dispositif de palier (42) qui est fixé en pivotement.
PCT/EP2020/073052 2019-08-21 2020-08-18 Machine électrique pour un véhicule à moteur Ceased WO2021032708A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102019212535.2A DE102019212535A1 (de) 2019-08-21 2019-08-21 Elektrische Maschine für ein Kraftfahrzeug
DE102019212535.2 2019-08-21

Publications (1)

Publication Number Publication Date
WO2021032708A1 true WO2021032708A1 (fr) 2021-02-25

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2020/073052 Ceased WO2021032708A1 (fr) 2019-08-21 2020-08-18 Machine électrique pour un véhicule à moteur

Country Status (2)

Country Link
DE (1) DE102019212535A1 (fr)
WO (1) WO2021032708A1 (fr)

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE549873C (de) * 1928-11-30 1932-05-04 Aeg Spinnzentrifugenmotor
DE2918763A1 (de) * 1979-05-09 1981-01-22 Kraftwerk Union Ag Lageranordnung fuer laeufer elektrischer maschinen, insbesondere fuer einen laeufer eines turbogenerators mit supraleitender feldwicklung
DE3538502A1 (de) * 1984-11-02 1986-05-28 Karsten Dipl.-Ing. 7148 Remseck Laing Taumelbar gelagerter laeufer
WO2003080927A1 (fr) * 2002-03-24 2003-10-02 Vomag Gmbh Dispositif de support d'un arbre
WO2006089835A1 (fr) * 2005-02-25 2006-08-31 Siemens Aktiengesellschaft Entrainement a moteur electrique
WO2009083362A1 (fr) * 2007-12-28 2009-07-09 Arcelik Anonim Sirketi Moteur électrique
US20170204904A1 (en) * 2016-01-20 2017-07-20 Summit Esp, Llc Electrical submersible motor radial support bearing
WO2019072487A1 (fr) * 2017-10-13 2019-04-18 Continental Automotive Gmbh Boîte de vitesses dotée d'une machine électrique intégrée

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2139379A (en) * 1934-10-06 1938-12-06 Us Electrical Motors Inc Interchangeable turbine pump head
WO2003084029A1 (fr) * 2002-04-01 2003-10-09 Nissan Motor Co., Ltd. Structure de refroidissement pour moteur electrique multicouches, a arbres multiples
JP4344681B2 (ja) * 2004-12-02 2009-10-14 本田技研工業株式会社 インナーロータ型回転電機
EP2933483A1 (fr) * 2014-04-15 2015-10-21 Siemens Aktiengesellschaft Système d'entraînement d'une éolienne

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE549873C (de) * 1928-11-30 1932-05-04 Aeg Spinnzentrifugenmotor
DE2918763A1 (de) * 1979-05-09 1981-01-22 Kraftwerk Union Ag Lageranordnung fuer laeufer elektrischer maschinen, insbesondere fuer einen laeufer eines turbogenerators mit supraleitender feldwicklung
DE3538502A1 (de) * 1984-11-02 1986-05-28 Karsten Dipl.-Ing. 7148 Remseck Laing Taumelbar gelagerter laeufer
WO2003080927A1 (fr) * 2002-03-24 2003-10-02 Vomag Gmbh Dispositif de support d'un arbre
WO2006089835A1 (fr) * 2005-02-25 2006-08-31 Siemens Aktiengesellschaft Entrainement a moteur electrique
WO2009083362A1 (fr) * 2007-12-28 2009-07-09 Arcelik Anonim Sirketi Moteur électrique
US20170204904A1 (en) * 2016-01-20 2017-07-20 Summit Esp, Llc Electrical submersible motor radial support bearing
WO2019072487A1 (fr) * 2017-10-13 2019-04-18 Continental Automotive Gmbh Boîte de vitesses dotée d'une machine électrique intégrée

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